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US4836055A - System for controlling a line pressure in an automatic transmission for motor vehicles - Google Patents

System for controlling a line pressure in an automatic transmission for motor vehicles Download PDF

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Publication number
US4836055A
US4836055A US07/177,493 US17749388A US4836055A US 4836055 A US4836055 A US 4836055A US 17749388 A US17749388 A US 17749388A US 4836055 A US4836055 A US 4836055A
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Prior art keywords
line pressure
signal
vehicle speed
pressure
control
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Expired - Lifetime
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US07/177,493
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Hosei Suzuki
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Subaru Corp
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Fuji Jukogyo KK
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Assigned to FUJI JUKOGYO KABUSHIKI KAISHA reassignment FUJI JUKOGYO KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SUZUKI, HOSEI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/14—Inputs being a function of torque or torque demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36—Inputs being a function of speed
    • F16H59/38—Inputs being a function of speed of gearing elements
    • F16H59/40—Output shaft speed

Definitions

  • the present invention relates to a system for controlling line pressure in an automatic transmission where the pressure is controlled dependent on vehicle speed and throttle opening degree by operating a solenoid operated valve provided in the system.
  • the line pressure is controlled by a pressure modifier valve actuated by governor pressure which changes with vehicle speed.
  • the line pressure is stepwisely changed from a high level value to a low level value in accordance with the vehicle speed. Namely, in a low vehicle speed range, where engine torque is large, the line pressure is at a high level and in a high vehicle speed range, where the torque becomes smaller, the line pressure is reduced.
  • Japanese Utility Model Laid Open No. 56-127141 discloses an automatic transmission comprising a hydraulic circuit having three shift valves and an electronic control circuit having a solenoid operated valve to which a signal dependent on vehicle speed and on engine load is applied.
  • the solenoid operated valve is arranged to produce control pressures of three levels.
  • the shift valves are operated by different control pressures respectively, so that the transmission ratio may be changed.
  • the object of the present invention is to provide a system for controlling line pressure in an automatic transmission device, wherein the proportion of the line pressure to engine torque is kept relatively constant at any vehicle speed so that pump loss and shock which occurs at the changing of the transmission ratio are reduced.
  • a system for controlling line pressure in a hydraulically operated automatic transmission for a motor vehicle comprising an engine load detector for producing a load signal dependent on load on an engine of the vehicle, a vehicle speed detector for producing a vehicle speed signal dependent on speed of the vehicle, a line pressure calculator responsive to the load signal and vehicle speed signal for producing a line pressure signal representing line pressure, and control signal generating means responsive to the line pressure signal for producing a control signal.
  • a hydraulic circuit of the automatic transmission has an electromagnetic valve operated by the control signal, for controlling pressure of a control oil in a hydraulic circuit of the automatic transmission, and a pressure regulator valve is provided in the hydraulic circuit and operated by the control oil to control line pressure, and the line pressure calculator produces the line pressure signal representing the necessary line pressure which increases with the load signal and decreases with the vehicle speed signal and has a constant value when the load signal and the vehicle speed signal exceed respective predetermined values so as to approximate the line pressure to torque of the engine.
  • the engine load detector is a throttle opening degree calculator
  • the control signal comprises pulses
  • the electromagnetic valve is a solenoid operated valve.
  • the system has further a pressure modifier valve operated by the control signal, for generating modifier pressure for operating the pressure regulator valve.
  • FIGS. 1a and 1b show a four-wheel drive power transmission system and a block diagram of a control unit provided in the system of the present invention
  • FIG. 2 is a schematic diagram of a hydraulic circuit for controlling line pressure
  • FIG. 3 is a graph showing characteristics of engine torque and line pressure at wide-open throttle
  • FIG. 4 is a graph showing a relationship between line pressure and throttle opening degree.
  • FIG. 5 is a graph showing characteristics of engine torque and line pressure in a conventional system.
  • an internal combustion engine E is mounted on a front portion of a vehicle.
  • a crankshaft 1 of the engine E is operatively connected with a torque converter 3 having a lockup clutch 2 of an automatic transmission A.
  • the automatic transmission A comprises the torque converter 3, and an automatic transmission device 5 operatively connected with the torque converter 3 through an input shaft 4.
  • the output of the automatic transmission device 5 is transmitted to an output shaft 6 on which a drive gear 7 is securely mounted, and the drive gear 7 engages with a driven gear 7'.
  • the driven gear 7' is securely mounted on a front drive shaft 8, which is integral with an drive pinion 8a engaged with a crown gear 9 of a final reduction device for the front wheels of the vehicle.
  • the output shaft 6 is connected to a rear drive shaft 11 through a transfer clutch 10 which is in a form of a fluid operated multiple-disc friction clutch.
  • the rear drive shaft 11 is further operatively connected to a final reduction device 13 for rear wheels of the vehicle through a propeller shaft 12.
  • the automatic transmission device 5 is supplied with pressurized oil from a hydraulic control device 14 which is provided under the front drive shaft 8.
  • the hydraulic control device 14 is controlled by a control unit 15 (FIG. 1b).
  • the control system is further provided with a throttle position sensor 16, vehicle speed sensor 17 and line pressure sensor 18 for controlling a solenoid operated valve provided in the hydraulic control device 14.
  • the circuit has a pressure regulator valve 21, a solenoid operated valve 19, a pressure modifier valve 22, and a pilot valve 23.
  • Oil from an oil pump 20 is supplied to pressure regulator valve 21.
  • the pressure regulator valve 21 is supplied with modifier pressure Pa from the pressure modifier valve 22 at the upper end.
  • An upper chamber of the pressure modifier valve 22 is applied with duty pressure Pb which is determined in accordance with the duty cycle of the solenoid operated valve 19.
  • the solenoid operated valve 19 which is operated by pulses from the control unit 15 opens to drain the oil from a drain port 30 when energized.
  • the pressure regulator valve 21 and the pressure modifier valve 22 are communicated with the pilot valve 23.
  • the control unit 15 for controlling the solenoid operated valve 19 comprises a throttle opening degree calculator 25 and a vehicle speed calculator 26 to which output signals of the throttle position sensor 16 and the vehicle speed sensor 17 are applied, respectively.
  • a throttle opening degree signal ⁇ calculated by the calculator 25, vehicle speed signal V calculated by the calculator 26 and present line pressure signal Po detected by the line pressure sensor 18 are applied to a line pressure calculator 27 which produces a corrected line pressure signal Pc.
  • the line pressure signal Pc represents necessary line pressure and is fed to a duty cycle calculator 28 where duty cycle D corresponding to the necessary line pressure is calculated. Therefore, the solenoid operated valve 19 is operated at the duty cycle D.
  • the line pressure P is controlled to increase with the increase of the throttle opening degree ⁇ and to decrease with the increase of the vehicle speed V in a low vehicle speed range.
  • FIG. 4 shows relationships between the line pressure P and the throttle opening degree ⁇ when the vehicle speed as a parameter is lower than vehicle speed V 1 (V ⁇ V 1 ).
  • V ⁇ V 1 vehicle speed
  • the throttle opening degree ⁇ is smaller than a predetermined degree ⁇ 1 ( ⁇ 1 )
  • the line pressure P is maintained at a predetermined value P 1 as shown by line 1 1 .
  • the line pressure P is calculated as follows.
  • the line pressure P is calculated as follows.
  • the line pressure P is a function of the throttle opening degree ⁇ .
  • the line pressure is kept constant at the value P H which is obtained by the following equation.
  • the present invention provides a line pressure control system where the proportion of line pressure to torque is maintained substantially constant at any vehicle speed. Accordingly, pump loss of an oil pump provided for the automatic transmission device is decreased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Control Of Driving Devices And Active Controlling Of Vehicle (AREA)

Abstract

A system for controlling line pressure has a line pressure calculator for producing a line pressure signal in response to load on an engine and vehicle speed, a control signal generator responsive to the line pressure signal for producing a control signal, and an electromagnetic valve operated by the control signal, for controlling pressure of control oil in a hydraulic circuit of an automatic transmission. A pressure regulator valve provided in the hydraulic circuit is operated by the control oil to control line pressure.

Description

BACKGROUND OF THE INVENTION
The present invention relates to a system for controlling line pressure in an automatic transmission where the pressure is controlled dependent on vehicle speed and throttle opening degree by operating a solenoid operated valve provided in the system.
In a conventional hydraulic circuit for an automatic transmission, the line pressure is controlled by a pressure modifier valve actuated by governor pressure which changes with vehicle speed. As shown in FIG. 5, the line pressure is stepwisely changed from a high level value to a low level value in accordance with the vehicle speed. Namely, in a low vehicle speed range, where engine torque is large, the line pressure is at a high level and in a high vehicle speed range, where the torque becomes smaller, the line pressure is reduced.
Japanese Utility Model Laid Open No. 56-127141 discloses an automatic transmission comprising a hydraulic circuit having three shift valves and an electronic control circuit having a solenoid operated valve to which a signal dependent on vehicle speed and on engine load is applied. The solenoid operated valve is arranged to produce control pressures of three levels. The shift valves are operated by different control pressures respectively, so that the transmission ratio may be changed.
However, in the line pressure control shown in FIG. 5, since the line pressure can only be kept at either of the two levels, there are two regions designated by A and B where line pressures are too high relative to the torque. In such regions, pump loss in an oil pump and shock which occurs at changing of the transmission ratio increase.
SUMMARY OF THE INVENTION
The object of the present invention is to provide a system for controlling line pressure in an automatic transmission device, wherein the proportion of the line pressure to engine torque is kept relatively constant at any vehicle speed so that pump loss and shock which occurs at the changing of the transmission ratio are reduced.
According to the present invention, there is provided a system for controlling line pressure in a hydraulically operated automatic transmission for a motor vehicle comprising an engine load detector for producing a load signal dependent on load on an engine of the vehicle, a vehicle speed detector for producing a vehicle speed signal dependent on speed of the vehicle, a line pressure calculator responsive to the load signal and vehicle speed signal for producing a line pressure signal representing line pressure, and control signal generating means responsive to the line pressure signal for producing a control signal.
A hydraulic circuit of the automatic transmission has an electromagnetic valve operated by the control signal, for controlling pressure of a control oil in a hydraulic circuit of the automatic transmission, and a pressure regulator valve is provided in the hydraulic circuit and operated by the control oil to control line pressure, and the line pressure calculator produces the line pressure signal representing the necessary line pressure which increases with the load signal and decreases with the vehicle speed signal and has a constant value when the load signal and the vehicle speed signal exceed respective predetermined values so as to approximate the line pressure to torque of the engine.
In an aspect of the invention, the engine load detector is a throttle opening degree calculator, the control signal comprises pulses, and the electromagnetic valve is a solenoid operated valve. The system has further a pressure modifier valve operated by the control signal, for generating modifier pressure for operating the pressure regulator valve.
The present invention will be more apparent from the following description made with reference to the accompanying drawings.
BRIEF DESCRIPTION OF DRAWINGS
FIGS. 1a and 1b show a four-wheel drive power transmission system and a block diagram of a control unit provided in the system of the present invention;
FIG. 2 is a schematic diagram of a hydraulic circuit for controlling line pressure;
FIG. 3 is a graph showing characteristics of engine torque and line pressure at wide-open throttle;
FIG. 4 is a graph showing a relationship between line pressure and throttle opening degree; and
FIG. 5 is a graph showing characteristics of engine torque and line pressure in a conventional system.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to FIG. 1, an internal combustion engine E is mounted on a front portion of a vehicle. A crankshaft 1 of the engine E is operatively connected with a torque converter 3 having a lockup clutch 2 of an automatic transmission A. The automatic transmission A comprises the torque converter 3, and an automatic transmission device 5 operatively connected with the torque converter 3 through an input shaft 4.
The output of the automatic transmission device 5 is transmitted to an output shaft 6 on which a drive gear 7 is securely mounted, and the drive gear 7 engages with a driven gear 7'. The driven gear 7' is securely mounted on a front drive shaft 8, which is integral with an drive pinion 8a engaged with a crown gear 9 of a final reduction device for the front wheels of the vehicle. The output shaft 6 is connected to a rear drive shaft 11 through a transfer clutch 10 which is in a form of a fluid operated multiple-disc friction clutch. The rear drive shaft 11 is further operatively connected to a final reduction device 13 for rear wheels of the vehicle through a propeller shaft 12.
The automatic transmission device 5 is supplied with pressurized oil from a hydraulic control device 14 which is provided under the front drive shaft 8. The hydraulic control device 14 is controlled by a control unit 15 (FIG. 1b). The control system is further provided with a throttle position sensor 16, vehicle speed sensor 17 and line pressure sensor 18 for controlling a solenoid operated valve provided in the hydraulic control device 14.
Referring to FIG. 2 showing a hydraulic circuit for controlling line pressure, the circuit has a pressure regulator valve 21, a solenoid operated valve 19, a pressure modifier valve 22, and a pilot valve 23. Oil from an oil pump 20 is supplied to pressure regulator valve 21. The pressure regulator valve 21 is supplied with modifier pressure Pa from the pressure modifier valve 22 at the upper end. An upper chamber of the pressure modifier valve 22 is applied with duty pressure Pb which is determined in accordance with the duty cycle of the solenoid operated valve 19. The solenoid operated valve 19 which is operated by pulses from the control unit 15 opens to drain the oil from a drain port 30 when energized. The pressure regulator valve 21 and the pressure modifier valve 22 are communicated with the pilot valve 23. When the duty cycle of the solenoid operated valve 19 increases, amount of drain oil increase, thereby reducing the duty pressure Pb. When duty pressure Pb reduces, a spool 22a rises to reduce the modifier pressure Pa. Accordingly, line pressure P regulated by the regulator valve 21 becomes lower. Thus, the line pressure P is controlled to an optimum value dependent on the driving conditions by controlling the duty cycle of the solenoid operated valve 19.
As shown in FIG. 1b, the control unit 15 for controlling the solenoid operated valve 19 comprises a throttle opening degree calculator 25 and a vehicle speed calculator 26 to which output signals of the throttle position sensor 16 and the vehicle speed sensor 17 are applied, respectively. A throttle opening degree signal θ calculated by the calculator 25, vehicle speed signal V calculated by the calculator 26 and present line pressure signal Po detected by the line pressure sensor 18 are applied to a line pressure calculator 27 which produces a corrected line pressure signal Pc. The line pressure signal Pc represents necessary line pressure and is fed to a duty cycle calculator 28 where duty cycle D corresponding to the necessary line pressure is calculated. Therefore, the solenoid operated valve 19 is operated at the duty cycle D.
The calculation for obtaining the line pressure P is described hereinafter with reference to FIGS. 3 and 4.
In the present invention the line pressure P is controlled to increase with the increase of the throttle opening degree θ and to decrease with the increase of the vehicle speed V in a low vehicle speed range. FIG. 3 shows a relationship between the line pressure P and vehicle speed V at wide-open throttle (θ=θw), as an example. When the vehicle speed V is lower than a predetermined speed V1, for example a vehicle speed at which the lockup clutch of the torque converter is released, the line pressure decreases linearly in accordance with the following equation.
P=f(P.sub.O -CV) (C is a constant)
When the vehicle speed V reaches the predetermined speed V1 so that the lockup clutch is locked, the line pressure P is kept at a value PH (P=PH). Accordingly, the characteristic of the line pressure P at wide-open throttle approximates that of engine torque F so that the proportion of the line pressure P to the torque F is substantially constant at any vehicle speed.
FIG. 4 shows relationships between the line pressure P and the throttle opening degree θ when the vehicle speed as a parameter is lower than vehicle speed V1 (V≦V1). When the throttle opening degree θ is smaller than a predetermined degree θ1 (θ≦θ1), the line pressure P is maintained at a predetermined value P1 as shown by line 11.
When the throttle opening degree θ is between the predetermined degree θ1 and another predetermined degree θ2 which is larger than the predetermined degree θ1 (θ1 <θ≦θ2), the line pressure P is calculated as follows.
P=f[(kaθ+kb)×(kc-kdV)] (ka to kd are constants)
Accordingly, the line pressure P increases with increase of the throttle opening degree θ, as shown by lines 12.
When the throttle opening degree θ exceeds the predetermined degree θ2 (θ>θ2), the line pressure P is calculated as follows.
P=f(ke-kgV) (ke and kg are constants)
Thus, the line pressure P is kept constant as shown by lines 13.
When the vehicle speed V exceeds the predetermined speed V1 (V>V1) while the throttle opening degree θ is below θ1, the line pressure P is constant at the pressure P1. When the throttle opening degree θ is between θ1 and θ2, the line pressure P is calculated in accordance with the following equation.
P=f[(kaθ+kb)×(kc-kdV.sub.1)]
Namely, the line pressure P is a function of the throttle opening degree θ. When the throttle opening degree θ becomes larger than the predetermined value θ2, the line pressure is kept constant at the value PH which is obtained by the following equation.
P.sub.H =f[(kaθ.sub.2 +kb)×(kc-kdV.sub.1)]
From the foregoing, it will be understood that the present invention provides a line pressure control system where the proportion of line pressure to torque is maintained substantially constant at any vehicle speed. Accordingly, pump loss of an oil pump provided for the automatic transmission device is decreased.
While the presently preferred embodiment of the present invention has been shown and described, it is to be understood that this disclosure is for the purpose of illustration and that various changes and modifications may be made without departing from the scope of the invention as set forth in the appended claims.

Claims (7)

What is claimed is:
1. A system for controlling line pressure in a hydraulically operated automatic transmission for a motor vehicle having an engine operatively connected to the transmission comprising:
a single engine load detector for producing a load signal dependent on load on the engine of the vehicle;
a vehicle speed detector for producing a vehicle speed signal dependent on speed of the vehicle;
a line pressure calculator responsive to the load signal and vehicle speed signal for producing a line pressure signal representing necessary line pressure;
control signal generating means responsive to the line pressure signal for producing a control signal corresponding to the line pressure signal;
an electromagnetic valve operated by the control signal, for controlling pressure of control oil in a hydraulic circuit of the automatic transmission;
a pressure regulator valve provided in the hydraulic circuit and operated by the control oil to control the line pressure in the transmission;
said line pressure calculator being arranged to produce the line pressure signal representing the necessary line pressure which increases with the load signal and decreases with the vehicle speed signal and has a constant value when the load signal and the vehicle speed signal exceed respective predetermined values, so as to approximate the line pressure to torque of the engine.
2. The system according to claim 1 wherein the engine load detector is a throttle opening degree calculator.
3. The system according to claim 1 wherein the control signal comprises pulses, and the electromagnetic valve is a solenoid operated valve.
4. The system according to claim 1 further comprising a pressure modifier valve operated by the control oil, for generating modifier pressure for operating the pressure regulator valve.
5. A system according to claim 1, further comprising
an oil pump provided in the hydraulic circuit, and
said line pressure calculator produces said line pressure signal such that the proportion of the necessary line pressure to engine torque is substantially constant, so as to prevent pump loss in said oil pump in the hydraulic circuit and shock from occurring at starting of increasing of the transmission ratio of the transmission at any vehicle speed.
6. A system according to claim 1, wherein
said line pressure calculator is further responsive to line pressure in the hydraulic circuit of the automatic transmission.
7. A system according to claim 1, wherein
said transmission includes a lockup clutch of a torque converter, and
one of said predetermined values represents a vehicle speed at which said lockup clutch of said torque converter is released, and wherein said line pressure calculator decreases said line pressure signal representing the necessary line pressure linearly with increasing vehicle speed below said one predetermined value.
US07/177,493 1987-04-13 1988-04-04 System for controlling a line pressure in an automatic transmission for motor vehicles Expired - Lifetime US4836055A (en)

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Application Number Priority Date Filing Date Title
JP62-091544 1987-04-13
JP62091544A JP2741023B2 (en) 1987-04-13 1987-04-13 Hydraulic control device for automatic transmission

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4939957A (en) * 1988-05-06 1990-07-10 Nissan Motor Co., Ltd. Line pressure control arrangement for automatic transmission
US5012696A (en) * 1988-10-19 1991-05-07 Fuji Jukogyo Kabushiki Kaisha Line pressure control system for a continuously variable transmission
US5086669A (en) * 1989-06-30 1992-02-11 Mazda Motor Corporation Line pressure controller for automatic transmission
US5107723A (en) * 1988-12-09 1992-04-28 Nissan Motor Co., Ltd. Select shock attenuation arrangement for an automatic automotive transmission
US5189931A (en) * 1990-09-04 1993-03-02 Aisin Aw Co., Ltd. Electronically controlled automatic transmission
US5305663A (en) * 1992-08-10 1994-04-26 Ford Motor Company Automatic transmission control system
US5549102A (en) * 1991-11-07 1996-08-27 Paul Ritzau Pari-Werk Gmbh Nebulizer, especially for application in devices for inhalation therapy
GB2313423A (en) * 1996-05-24 1997-11-26 Luk Getriebe Systeme Gmbh Control of fluid pressure for operating torque-transmitting components in a motor vehicle transmission
US6022293A (en) * 1998-10-08 2000-02-08 Chrysler Corporation Electronic control of transmission line pressure
US20040241848A1 (en) * 2003-05-28 2004-12-02 Samsung Electronics Co., Ltd. Method of detecting microorgan ISMS using labelled electron acceptors
US20070142173A1 (en) * 2005-12-21 2007-06-21 Toyota Jidosha Kabushiki Kaisha Line pressure control apparatus and line pressure control method for automatic transmission
US7377827B1 (en) 2003-06-20 2008-05-27 Sturdy Corporation Marine propulsion shift control
US8958963B2 (en) 2012-03-26 2015-02-17 Cnh Industrial America Llc System and method for controlling the pressure of hydraulic fluid supplied within a work vehicle transmission

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US4928544A (en) * 1989-06-19 1990-05-29 Eaton Corporation Dual pressure pressurized fluid actuated shifting mechanism
DE19735820B4 (en) 1997-08-18 2005-08-18 Daimlerchrysler Ag Switching device of a change gear with pressure control valves for the working pressure and a supply pressure
JP3475796B2 (en) * 1998-07-24 2003-12-08 日産自動車株式会社 Line pressure control device for automatic transmission

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US3680410A (en) * 1969-09-13 1972-08-01 Toyota Motor Co Ltd Actuating oil pressure control system for torque converter automatic transmission
US3688609A (en) * 1970-11-12 1972-09-05 Borg Warner Overdrive electronic control system
US3776048A (en) * 1971-02-08 1973-12-04 Nissan Motor Automatic power transmission control system
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JPS56127141A (en) * 1980-03-08 1981-10-05 Michiyuki Nedachi Heat storage tank for solar heat air conditioner combined with hot-water supply
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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4939957A (en) * 1988-05-06 1990-07-10 Nissan Motor Co., Ltd. Line pressure control arrangement for automatic transmission
US5012696A (en) * 1988-10-19 1991-05-07 Fuji Jukogyo Kabushiki Kaisha Line pressure control system for a continuously variable transmission
US5107723A (en) * 1988-12-09 1992-04-28 Nissan Motor Co., Ltd. Select shock attenuation arrangement for an automatic automotive transmission
US5086669A (en) * 1989-06-30 1992-02-11 Mazda Motor Corporation Line pressure controller for automatic transmission
DE4129286B4 (en) * 1990-09-04 2006-12-21 Aisin AW Co., Ltd., Anjo Electronically controlled automatic transmission
US5189931A (en) * 1990-09-04 1993-03-02 Aisin Aw Co., Ltd. Electronically controlled automatic transmission
US5549102A (en) * 1991-11-07 1996-08-27 Paul Ritzau Pari-Werk Gmbh Nebulizer, especially for application in devices for inhalation therapy
US5413539A (en) * 1992-08-10 1995-05-09 Ford Motor Company Control system for controlling engagement of an automatic transmission torque converter clutch
US5305663A (en) * 1992-08-10 1994-04-26 Ford Motor Company Automatic transmission control system
GB2313423A (en) * 1996-05-24 1997-11-26 Luk Getriebe Systeme Gmbh Control of fluid pressure for operating torque-transmitting components in a motor vehicle transmission
GB2313423B (en) * 1996-05-24 2000-12-06 Luk Getriebe Systeme Gmbh Fluid-operated apparatus for operating adjustable constituents of motor vehicles
US6022293A (en) * 1998-10-08 2000-02-08 Chrysler Corporation Electronic control of transmission line pressure
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US7377827B1 (en) 2003-06-20 2008-05-27 Sturdy Corporation Marine propulsion shift control
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Also Published As

Publication number Publication date
GB2207716B (en) 1990-12-19
JPS63259257A (en) 1988-10-26
JP2741023B2 (en) 1998-04-15
DE3812003C2 (en) 1991-12-19
DE3812003A1 (en) 1988-11-03
GB8808549D0 (en) 1988-05-11
GB2207716A (en) 1989-02-08

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